JPH0231615Y2 - - Google Patents
Info
- Publication number
- JPH0231615Y2 JPH0231615Y2 JP1985199349U JP19934985U JPH0231615Y2 JP H0231615 Y2 JPH0231615 Y2 JP H0231615Y2 JP 1985199349 U JP1985199349 U JP 1985199349U JP 19934985 U JP19934985 U JP 19934985U JP H0231615 Y2 JPH0231615 Y2 JP H0231615Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- leaf valve
- washer plate
- shock absorber
- leaf
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000006096 absorbing agent Substances 0.000 claims description 22
- 230000035939 shock Effects 0.000 claims description 22
- 229910000639 Spring steel Inorganic materials 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 238000013016 damping Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000004080 punching Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/14—Check valves with flexible valve members
- F16K15/148—Check valves with flexible valve members the closure elements being fixed in their centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/14—Check valves with flexible valve members
- F16K15/148—Check valves with flexible valve members the closure elements being fixed in their centre
- F16K15/1481—Check valves with flexible valve members the closure elements being fixed in their centre with biasing means in addition to material resiliency, e.g. spring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K2200/00—Details of valves
- F16K2200/30—Spring arrangements
- F16K2200/305—Constructional features of springs
- F16K2200/3053—Helicoidal springs of variable pitch, diameter or spring rate
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7879—Resilient material valve
- Y10T137/7888—With valve member flexing about securement
- Y10T137/789—Central mount
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
- Y10T29/49908—Joining by deforming
- Y10T29/49938—Radially expanding part in cavity, aperture, or hollow body
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、油圧緩衝器に係り、とくにそのベー
スバルブ部分の構造に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a hydraulic shock absorber, and particularly to the structure of its base valve portion.
車両のサスペンシヨン機構には、上下振動を緩
衝するために、油圧緩衝器が用いられる。油圧緩
衝器の構造自体は公知であり、後述する本考案の
説明の一部からも明らかなように、通常内筒と外
筒とを有し、内筒と外筒間にリザーバ室が設けら
れ、内筒内の油圧室とリザーバ室とは内筒底部に
装着したベースバルブによつて油の流通制御が可
能に区画されている。内筒内にはピストンバルブ
が軸芯に沿つて移動可能に挿入され、内筒内を油
の流通制御が可能に２つに区画している。ピスト
ンバルブにはピストンロツドが取付けられ、内筒
の上端に取付けた端板材を貫通して外方に延び機
器への連結手段を形成している。
Hydraulic shock absorbers are used in vehicle suspension mechanisms to dampen vertical vibrations. The structure of a hydraulic shock absorber itself is well known, and as will be clear from part of the explanation of the present invention described later, it usually has an inner cylinder and an outer cylinder, and a reservoir chamber is provided between the inner cylinder and the outer cylinder. The hydraulic chamber and the reservoir chamber in the inner cylinder are separated by a base valve attached to the bottom of the inner cylinder so that oil flow can be controlled. A piston valve is inserted into the inner cylinder so as to be movable along the axis, and the inner cylinder is divided into two parts so as to be able to control the flow of oil. A piston rod is attached to the piston valve and extends outwardly through an end plate attached to the upper end of the inner cylinder to form a connection to the equipment.
ベースバルブ部分の構造は、ベースバルブ１
と、該ベースバルブに開口したポートを弾性的に
開閉する環状のリーフバルブと、リーフバルブの
底面側の内周部位に配設された環状のリーフバル
ブシートと、リーフバルブシートの底面側に配設
された環状のワツシヤプレートと、環状のベース
バルブ、リーフバルブ、リーフバルブシートおよ
びワツシヤプレートに嵌入する軸部を備えたバル
ブガイドとを有し、バルブガイドの一端に設けた
フランジ部と他方の軸端部に軸方向の圧縮力をか
けて形成したかしめ部との間に、バルブケース、
リーフバルブ、リーフバルブシートおよびワツシ
ヤプレートを挾持させたものから構成される。 The structure of the base valve part is base valve 1.
, an annular leaf valve that elastically opens and closes a port opened in the base valve, an annular leaf valve seat disposed on the inner periphery of the bottom side of the leaf valve, and an annular leaf valve seat disposed on the bottom side of the leaf valve seat. It has an annular washer plate provided therein, a valve guide having an annular base valve, a leaf valve, a leaf valve seat, and a shaft part that fits into the washer plate, and a flange part provided at one end of the valve guide. The valve case,
Consists of a leaf valve, a leaf valve seat, and a washer plate held in place.
上記構造において、ベースバルブは、通常焼結
品から成る。焼結品の場合、バルブガイドの軸部
が挿通する内周孔の角部等は、型打抜き時にかけ
てしまうので、従来、第４図に示すように、ベー
スバルブ１００の内周角部には、上、下面１０
２，１０４から中央に向つて後退するように形成
した段付部１０６，１０８が設けられている。
In the above structure, the base valve is usually made of a sintered product. In the case of a sintered product, the corners of the inner circumferential hole through which the valve guide shaft is inserted are damaged during die punching, so conventionally, as shown in FIG. 4, the inner circumferential corner of the base valve 100 is , top, bottom 10
Stepped portions 106 and 108 are provided so as to recede from 2 and 104 toward the center.
バルブガイド１１０のかしめ部１１２は、バル
ブガイド１１０とベースバルブ１００との回転防
止のため、バルブガイド１１０に大きな軸力をか
けてかしめている。かしめ力が大きいので、かし
め時に、ベースバルブ１００のシート面１１４の
段付き部１０６に過大な軸力が働き、ワツシヤプ
レート１１６の変形および平面度に沿つて、リー
フバルブ１１８が変形し、リーフバルブ１１８に
均一な軸力がかからなくなつて、リーフバルブ１
１８間に隙間１２０が発生して、所期の減衰力が
得られないことがある。また、ワツシヤプレート
１１６の平面度にそつて、軸力かけ時にリーフバ
ルブ１１８が変形するので、これによつても上記
と同様の問題が発生してしまう。 The caulking portion 112 of the valve guide 110 is caulked by applying a large axial force to the valve guide 110 in order to prevent the valve guide 110 and the base valve 100 from rotating. Since the caulking force is large, an excessive axial force acts on the stepped portion 106 of the seat surface 114 of the base valve 100 during caulking, and the leaf valve 118 deforms along with the deformation and flatness of the washer plate 116, causing the leaf Since uniform axial force is no longer applied to the valve 118, the leaf valve 1
A gap 120 may occur between 18 and the desired damping force may not be obtained. Further, since the leaf valve 118 is deformed when an axial force is applied in accordance with the flatness of the washer plate 116, the same problem as described above occurs.
本考案は、バルブガイドのかしめ部時に、大き
な軸力が負荷されたときのリーフバルブの変形を
抑え、リーフバルブ変形による減衰力の不安定化
を防止することを目的とする。 The present invention aims to suppress the deformation of the leaf valve when a large axial force is applied to the crimped portion of the valve guide, and to prevent the damping force from becoming unstable due to the deformation of the leaf valve.
上記目的に沿う本考案の油圧緩衝器は、緩衝器
内筒の底部に装着され底面側内周に段付部を形成
した環状のベースバルブと、該ベースバルブに開
口したポートを弾性的に開閉する環状のリーフバ
ルブと、該リーフバルブの底面側の内周部位に配
設された環状のリーフバルブシートと、該リーフ
バルブシートの底面側に配設された環状のワツシ
ヤプレートと、前記環状のベースバルブ、リーフ
バルブ、リーフバルブシートおよびワツシヤプレ
ートに嵌入する軸部を備えたバルブガイドとを有
し、前記バルブガイドの一端に設けたフランジ部
と他方の軸端部に軸方向の圧縮力をかけて形成し
たかしめ部との間に前記ベースバルブ、リーフバ
ルブ、リーフバルブシートおよびワツシヤプレー
トを挾持させた油圧緩衝器において、前記ワツシ
ヤプレートの前記リーフバルブ側の内周角部に前
記ベースバルブの段付部と同程度の大きさの面取
りを設けたものから成る。
The hydraulic shock absorber of the present invention that meets the above objectives includes an annular base valve that is attached to the bottom of the shock absorber inner cylinder and has a stepped part formed on the inner periphery of the bottom surface, and a port opened to the base valve that elastically opens and closes. an annular leaf valve, an annular leaf valve seat disposed on the inner circumference of the bottom side of the leaf valve, an annular washer plate disposed on the bottom side of the leaf valve seat, and an annular washer plate disposed on the bottom side of the leaf valve seat; a base valve, a leaf valve, a leaf valve seat, and a valve guide having a shaft portion that fits into the washer plate, and a flange portion provided at one end of the valve guide and an axial compression portion at the other shaft end portion. In the hydraulic shock absorber, the base valve, the leaf valve, the leaf valve seat, and the washer plate are sandwiched between the caulked portion formed by applying force, and the inner circumferential corner of the washer plate on the leaf valve side is The base valve is provided with a chamfer of approximately the same size as the stepped portion of the base valve.
上記油圧緩衝器においては、ワツシヤプレート
に面取りを設けたので、バルブガイドにかしめ部
を形成する際、ワツシヤプレートに大きな軸力が
作用しても、リーフバルブ内周縁に軸力がかから
ないので、リーフバルブがベースバルブの段付部
内に押し込まれるようなリーフバルブの変形は生
じない。このため、リーフバルブの変形は抑えら
れ、油圧緩衝器作動時に、ベースバルブシート面
にリーフバルブから均一な軸力が働き、安定した
減衰力が得られる。
In the above hydraulic shock absorber, since the washer plate is chamfered, even if a large axial force is applied to the washer plate when forming the caulked part on the valve guide, no axial force is applied to the inner peripheral edge of the leaf valve. , deformation of the leaf valve such that the leaf valve is pushed into the stepped portion of the base valve does not occur. Therefore, deformation of the leaf valve is suppressed, and when the hydraulic shock absorber is activated, a uniform axial force is applied from the leaf valve to the base valve seat surface, resulting in a stable damping force.
以下に、本考案に係る油圧緩衝器の望ましい実
施例を、図面を参照して説明する。
Hereinafter, preferred embodiments of the hydraulic shock absorber according to the present invention will be described with reference to the drawings.
第１図ないし第３図は本考案の実施例を示して
いる。油圧緩衝器２は、内筒４と、内筒４と同一
軸芯を有するように配設された外筒６とを有す
る。内筒４と外筒６との間にはリザーバ室８が画
成され、リザーバ室８には油と上部に気体とが入
つており、内筒４内には油が入つている。内筒４
の底部にはベースバルブ１０が装着され、内筒４
内の室とリザーバ室８とを、油の流通制御が可能
に画成している。内筒４内にはピストンバルブ１
２が軸芯に沿つて移動可能に挿入されており、ピ
ストンバルブ１２は内筒４内を、油の流通制御が
可能に、２つの油室すなわちＡ室１４、Ｂ室１６
に画成している。 1 to 3 show an embodiment of the invention. The hydraulic shock absorber 2 has an inner cylinder 4 and an outer cylinder 6 arranged so as to have the same axis as the inner cylinder 4. A reservoir chamber 8 is defined between the inner cylinder 4 and the outer cylinder 6, and the reservoir chamber 8 contains oil and gas in the upper part, and the inner cylinder 4 contains oil. Inner cylinder 4
A base valve 10 is attached to the bottom of the inner cylinder 4.
The inner chamber and the reservoir chamber 8 are defined so that oil distribution can be controlled. There is a piston valve 1 inside the inner cylinder 4.
2 is inserted so as to be movable along the axis, and the piston valve 12 has two oil chambers, a chamber A 14 and a chamber B 16, so as to control the flow of oil within the inner cylinder 4.
It is defined in
ピストンバルブ１２は、Ａ室１４、Ｂ室１６を
連通可能な２つのオリフイスＡ１８、オリフイス
Ｂ２０を備えている。オリフイスＡ１８、オリフ
イスＢ２０はノンリターンバルブ２２によつて開
閉が制御される。オリフイスＡ１８にはリーフバ
ルブ２４が設けられ、リーフバルブ２４は、油室
Ｂ１６の圧力が油室Ａ１４の圧力よりもかなり高
くなつたときに、開いてＢ室１６からＡ室１４へ
と油を流す。ピストンバルブ１２にはピストンロ
ツド６２が取付けられ、内筒４の上端の端板を貫
通して外方に延びている。 The piston valve 12 includes two orifices A18 and orifice B20 that can communicate the A chamber 14 and the B chamber 16. The opening and closing of the orifice A18 and the orifice B20 are controlled by a non-return valve 22. The orifice A18 is provided with a leaf valve 24, and the leaf valve 24 opens to allow oil to flow from the B chamber 16 to the A chamber 14 when the pressure in the oil chamber B16 becomes considerably higher than the pressure in the oil chamber A14. . A piston rod 62 is attached to the piston valve 12 and extends outwardly through an end plate at the upper end of the inner cylinder 4.
ベースバルブ１０は、オリフイスＣ２６、オリ
フイスＤ２８から成る２種類のポートを有してい
る。オリフイスＣ２６、オリフイスＤ２８のＡ室
１４側にはノンリターンバルブ３０が設けられて
いる。ノンリターン３０はばね３６によつてベー
スバルブ１０に押しつけられている。オリフイス
Ｃ２６のリザーバ室８側には、ばね鋼の環状平板
から成るリーフバルブ３２が設けられ、オリフイ
スＣ２６を通る油の流れを制御する。オリフイス
Ｄ２８の上端には、常時開の小面積のオリフイス
Ｅ３４が形成されている。 The base valve 10 has two types of ports, an orifice C26 and an orifice D28. A non-return valve 30 is provided on the A chamber 14 side of the orifice C26 and the orifice D28. The non-return 30 is pressed against the base valve 10 by a spring 36. A leaf valve 32 made of an annular flat plate of spring steel is provided on the reservoir chamber 8 side of the orifice C26 to control the flow of oil through the orifice C26. A small-area orifice E34 that is always open is formed at the upper end of the orifice D28.
ベースバルブ１０は環状体に形成され中央に軸
芯方向に延びる貫通孔を有する。ベースバルブ１
０の下端面はリーフバルブ３２が圧接されるシー
ト面３８を形成している。リーフバルブ３２の下
面には、その中央部近傍に環状の平板から成るリ
ーフバルブシート４０が接触されている。リーフ
バルブシート４０の下面側には、さらに環状の平
板から成るワツシヤプレート４２が接触されてい
る。ベースバルブ１０、リーフバルブ３２、リー
フバルブシート４０、ワツシヤプレート４２のそ
れぞれの中央の貫通孔には、バルブガイド４４の
軸部４６が挿通される。バルブガイド４４のＡ室
１４側の端部には半径方向に膨出したフランジ部
４８が形成され、バルブガイド４４のリザーバ室
８側の端部には、軸部４６に軸方向圧縮力をかけ
てかしめたかしめ部５０が形成される。ベースバ
ルブ１０、リーフバルブ３２、リーフバルブシー
ト４０、ワツシヤプレート４２は、バルブガイド
４４のフランジ部４８とかしめ部５０によつて挾
持されている。かしめ部５０は、軸部４６にベー
スバルブ１０、リーフバルブ３２、リーフバルブ
シート４０、ワツシヤプレート４２を装着した
後、軸部４６に軸方向圧縮力をかけて形成され
る。 The base valve 10 is formed into an annular body and has a through hole extending in the axial direction at the center. Base valve 1
The lower end surface of the leaf valve 32 forms a seat surface 38 to which the leaf valve 32 is pressed. A leaf valve seat 40 made of an annular flat plate is in contact with the lower surface of the leaf valve 32 near its center. Further, a washer plate 42 made of an annular flat plate is in contact with the lower surface side of the leaf valve seat 40. The shaft portion 46 of the valve guide 44 is inserted through the central through hole of each of the base valve 10, the leaf valve 32, the leaf valve seat 40, and the washer plate 42. A radially bulging flange portion 48 is formed at the end of the valve guide 44 on the A chamber 14 side, and an axial compressive force is applied to the shaft portion 46 at the end of the valve guide 44 on the reservoir chamber 8 side. A tightly caulked caulked portion 50 is formed. The base valve 10, the leaf valve 32, the leaf valve seat 40, and the washer plate 42 are held between the flange portion 48 and the caulking portion 50 of the valve guide 44. The caulking portion 50 is formed by applying an axial compressive force to the shaft portion 46 after attaching the base valve 10, leaf valve 32, leaf valve seat 40, and washer plate 42 to the shaft portion 46.
ベースバルブ１０は、通常焼結材によつて構成
されるが、焼結品の場合、エツジ部は型打抜時に
かけてしまうので、内周側のコーナー部に、ベー
スバルブ１０の上下面から後退させた段付き部５
２，５４が形成される。 The base valve 10 is usually made of sintered material, but in the case of a sintered product, the edges are cut out during die punching, so the edges are retracted from the upper and lower surfaces of the base valve 10 at the inner corner. Stepped part 5
2,54 are formed.
ワツシヤプレート４２には、拡大して示した第
２図に明瞭に示されているように、軸部４６が貫
通すく内周の、リーフバルブシート４０側のコー
ナに、全周にわたつて、面取り５６が設けられて
いる。面取り５６の半径方向の大きさｂは、バル
ブガイド４４の段付部５２の半径方向寸法ａと等
しいかまたはほぼ等しい大きさとなつている。す
なわちａ＝ｂかａ≒ｂである。 As clearly shown in the enlarged view of FIG. 2, the washer plate 42 has a shaft portion 46 penetrating therethrough, at the corner on the leaf valve seat 40 side of the inner circumference, over the entire circumference. A chamfer 56 is provided. The radial size b of the chamfer 56 is equal to or approximately the same as the radial size a of the stepped portion 52 of the valve guide 44 . That is, a=b or a≈b.
ワツシヤプレート４２の内周縁のかしめ部５０
側には、同様に面取り５８が設けられている。た
だし、面取り５８は必須のものではない。面取り
５８が設けられる場合は、面取り５８の半径方向
寸法を、面取り５６の半径方向寸法ｂに一致させ
ることが望ましい。 Caulking portion 50 on the inner peripheral edge of the washer plate 42
A chamfer 58 is likewise provided on the side. However, the chamfer 58 is not essential. If a chamfer 58 is provided, it is desirable that the radial dimension of the chamfer 58 corresponds to the radial dimension b of the chamfer 56.
ワツシヤプレート４２の、軸部４６貫通孔に
は、その内周に軸部４６の外周と摺接するガイド
部６０が残され、ワツシヤプレート４２ががたつ
かないようにガイド部６０は必要な寸法Ｃを有し
ている。 A guide portion 60 is left on the inner periphery of the through hole of the shaft portion 46 of the washer plate 42, and the guide portion 60 is in sliding contact with the outer periphery of the shaft portion 46. It has dimension C.
ワツシヤプレート４２は、かしめ部５０のかし
め時にかかる大きな軸力を受けて表面が変形しに
くいように、ばね鋼等の変形しにくい材料から構
成されている。 The washer plate 42 is made of a material that does not easily deform, such as spring steel, so that its surface is not easily deformed by the large axial force applied when the caulking portion 50 is caulked.
つぎに、上記のように構成された本考案の油圧
緩衝器における作用について説明する。 Next, the operation of the hydraulic shock absorber of the present invention configured as described above will be explained.
緩衝作用については知られているところである
が、説明しておくとつぎの通りである。 Although the buffering effect is well known, it can be explained as follows.
まず、バウンド時、すなわち縮み行程時におい
て、ピストンロツド６２の下降速度が速いとき
は、Ａ室１４の圧力が高いため、Ａ室１４の油は
ベースバルブ１０のリーフバルブ３２を押し下げ
てオリフイスＣ２６を通りリザーバ室８に流れ
る。一方、ピストンバルブ１２上部に流れる油
は、ピストンバルブ１２のノンリターンバルブ２
２を押し上げてオリフイスＢ２０を通りＢ室１６
へと流れる。このときのベースバルブ１０側の油
の流動抵抗がバウンド時の減衰力となる。 First, when the piston rod 62 descends at a high speed during bounce, that is, during the contraction stroke, the pressure in the A chamber 14 is high, so the oil in the A chamber 14 pushes down the leaf valve 32 of the base valve 10 and passes through the orifice C26. It flows into the reservoir chamber 8. On the other hand, the oil flowing to the upper part of the piston valve 12 is transferred to the non-return valve 2 of the piston valve 12.
2 and pass through orifice B20 to room B 16.
flows to. The flow resistance of the oil on the base valve 10 side at this time becomes the damping force at the time of bounce.
バウンド時で、ピストンロツド６２の下降速度
が遅いときは、Ａ室１４の圧力が低いため、Ａ室
１４の油はベースバルブ１０のリーフバルブ３２
を押し下げられず、ベースバルブ１０の上面の小
さなオリフイスＥ３４を通りリザーバ室８に流れ
る。一方、ピストンバルブ１２上部に流れる油
は、ピストンバルブ１２上部とＡ室１４の圧力差
によつてノンリターンバルブ２２を押し上げて、
油は上記と同様にオリフイスＢ２０を通りＢ室１
６へと流れる。 When the piston rod 62 descends slowly during bounce, the pressure in the A chamber 14 is low, so the oil in the A chamber 14 flows through the leaf valve 32 of the base valve 10.
is not pushed down and flows into the reservoir chamber 8 through the small orifice E34 on the top surface of the base valve 10. On the other hand, the oil flowing to the upper part of the piston valve 12 pushes up the non-return valve 22 due to the pressure difference between the upper part of the piston valve 12 and the A chamber 14.
Oil passes through orifice B20 and enters chamber B1 in the same way as above.
Flows to 6.
リバウンド時、すなわち伸び行程時には、ピス
トンロツド６２の上昇速度が速いときは、リザー
バ室８とＡ室１４の圧力差によつてベースバルブ
１０のノンリターンバルブ３０が押し上げられ
て、油はリザーバ室８からオリフイスＤ２８を通
つてＡ室１４へと流れる。一方、ピストンバルブ
１２上部の圧力が高くなり、ピストンバルブ１２
のリーフバルブ２４を押し下げて油はオリフイス
Ａ１８を通つてＡ室１４に流れる。このときのピ
ストンバルブ１２側の油の流動抵抗がリバウンド
時の減衰力となる。 During rebound, that is, during the extension stroke, when the rising speed of the piston rod 62 is fast, the non-return valve 30 of the base valve 10 is pushed up due to the pressure difference between the reservoir chamber 8 and the A chamber 14, and the oil is removed from the reservoir chamber 8. It flows into the A chamber 14 through the orifice D28. On the other hand, the pressure above the piston valve 12 increases, and the piston valve 12
The leaf valve 24 is pushed down and oil flows into the A chamber 14 through the orifice A18. The flow resistance of the oil on the piston valve 12 side at this time becomes the damping force at the time of rebound.
リバウンド時のピストンロツド６２の上昇速度
が遅いときは、リザーバ室８とＡ室１４との圧力
差によつて、ベースバルブ１０のノンリターンバ
ルブ３０が押し上げられて油はリザーバ室８から
オリフイスＤ２８を通つてＡ室１４に流れる。一
方、ピストンバルブ１２上部圧力が低いため、ピ
ストンバルブ１２のリーフバルブ２４を押し下げ
ることができず、ピストンバルブ１２上面の小さ
なオリフイスＦ（図示略）を通りＡ室１４に流れ
る。 When the rising speed of the piston rod 62 during rebound is slow, the pressure difference between the reservoir chamber 8 and the A chamber 14 pushes up the non-return valve 30 of the base valve 10, causing oil to flow from the reservoir chamber 8 through the orifice D28. and flows into the A room 14. On the other hand, since the pressure above the piston valve 12 is low, the leaf valve 24 of the piston valve 12 cannot be pushed down, and the air flows into the A chamber 14 through a small orifice F (not shown) on the top surface of the piston valve 12.
上記のようにベースバルブ１０のリーフバルブ
３２は、バウンド時、リバウンド時に減衰作用を
発生させる重要な機能を有している。したがつ
て、第４図に示したように、リーフバルブ３２が
変形したりすることは許されず、軸方向に均一な
力でシート面３８に押しつけられる必要がある。 As described above, the leaf valve 32 of the base valve 10 has an important function of generating a damping effect during bounce and rebound. Therefore, as shown in FIG. 4, the leaf valve 32 is not allowed to be deformed and must be pressed against the seat surface 38 with a uniform force in the axial direction.
つぎにリーフバルブ３２の油圧緩衝器２製造時
の変形防止作用について説明する。前記の如くバ
ルブガイド４４の軸部４６は軸方向圧縮力をかけ
られてかしめ部５０が形成されるが、このとき、
従来は、ワツシヤプレート４２、リーフバルブシ
ート４０を介してリーフバルブ３２に圧縮力が伝
わつていた。しかし、本考案ではワツシヤプレー
ト４２に面取り５６が設けられるので、内周部に
おいてリーフバルブ３２は圧縮力を受けず、バル
ブガイド４４の段付部５２に押し込まれて変形す
ることはない。したがつて、かしめ部５０形成時
のリーフバルブ３２の変形、およびワツシヤプレ
ート４２およびリーフバルブプレート４０の変形
による不均一な荷重のかかりが避けられる。この
ため、リーフバルブ３２は軸方向に均一に、ベー
スバルブ１０のシート面３８に圧接され、油のも
れ等による油圧緩衝作用の乱れを生じさせない。 Next, the deformation prevention effect of the leaf valve 32 during manufacture of the hydraulic shock absorber 2 will be explained. As described above, the axial compressive force is applied to the shaft portion 46 of the valve guide 44 to form the caulked portion 50, but at this time,
Conventionally, compressive force was transmitted to the leaf valve 32 via the washer plate 42 and the leaf valve seat 40. However, in the present invention, since the washer plate 42 is provided with a chamfer 56, the leaf valve 32 is not subjected to compressive force at the inner peripheral portion, and is not deformed by being pushed into the stepped portion 52 of the valve guide 44. Therefore, deformation of the leaf valve 32 during formation of the caulked portion 50 and application of uneven loads due to deformation of the washer plate 42 and the leaf valve plate 40 can be avoided. Therefore, the leaf valve 32 is pressed against the seat surface 38 of the base valve 10 uniformly in the axial direction, and the hydraulic damping effect is not disturbed due to oil leakage or the like.
また、ワツシヤプレート４２に、かしめ部５０
側にも、面取り５６と同一形状の面取り５８を形
成しておくと、ワツシヤプレート４２の表裏の区
別がなくなり、ワツシヤプレート４２を表裏を逆
にして軸部４６に挿通しないように配慮する必要
がなくなり、製造を容易にする。 Additionally, a caulking portion 50 is attached to the washer plate 42.
If a chamfer 58 having the same shape as the chamfer 56 is formed on the side as well, there will be no distinction between the front and back of the washer plate 42, and care must be taken not to insert the washer plate 42 upside down into the shaft portion 46. This eliminates the need and makes manufacturing easier.
上記のように、２つの面取り５６，５８を設け
ても、ワツシヤプレート４２はその内周に必要な
高さＣのガイド部６０を有しているので、ワツシ
ヤプレート４２ががたつくことも防止される。 As described above, even if the two chamfers 56 and 58 are provided, the washer plate 42 has the guide portion 60 of the required height C on its inner circumference, so the washer plate 42 is prevented from wobbling. be done.
また、ワツシヤプレート４２は、変形しにくい
ばね鋼より成るので、かしめ部５０形成時、ワツ
シヤプレート４２自体が全体的に湾曲変形するこ
とが防止され、ワツシヤプレート４２の変形によ
つてリーフバルブ３２に不均一な荷重が作用する
ことも防止され、上記の軸方向均一荷重が促進さ
れる。 Further, since the washer plate 42 is made of spring steel that is difficult to deform, the washer plate 42 itself is prevented from being deformed as a whole when the caulking portion 50 is formed. It is also prevented that an uneven load is applied to the valve 32, and the above-mentioned uniform load in the axial direction is promoted.
以上説明したように、本考案の油圧緩衝器２
は、そのワツシヤプレート４２の内周コーナに面
取り５６を設けるようにしたので、本考案による
ときは、リーフバルブ３２が、ベースバルブ１０
の段付部５２で変形することなく、ベースバルブ
１０のシート面３８に均一に軸力が働き、安定し
た減衰力を得ることができる。
As explained above, the hydraulic shock absorber 2 of the present invention
Since a chamfer 56 is provided on the inner circumferential corner of the washer plate 42, when according to the present invention, the leaf valve 32 is similar to the base valve 10.
Axial force acts uniformly on the seat surface 38 of the base valve 10 without being deformed by the stepped portion 52, and a stable damping force can be obtained.
また、ワツシヤプレート４２に変形しにくい硬
い材料が使用される場合は、かしめ軸力が負荷さ
れてもワツシヤプレート４２は変形しにくく、上
記の効果が助長される。 Furthermore, if a hard material that is not easily deformed is used for the washer plate 42, the washer plate 42 will not be easily deformed even if the caulking axial force is applied, and the above effect will be enhanced.
さらに、ワツシヤプレート４２に上、下面に面
取り５６，５８を設ければ、ワツシヤプレート４
２組付時の表裏の区別がなくなり、組付けを容易
化できる。 Furthermore, if chamfers 56 and 58 are provided on the upper and lower surfaces of the washer plate 42, the washer plate 4
There is no distinction between the front and back when assembling the two, making assembly easier.
第１図は本考案の一実施例に係る油圧緩衝器の
ベースバルブ部分の断面図、第２図は第１図のう
ちワツシヤプレートとその近傍の拡大断面図、第
３図は第１図の油圧緩衝器のピストンバルブ以下
の断面図、第４図は従来の油圧緩衝器のワツシヤ
プレート近傍の断面図、である。
４……内筒、６……外筒、８……リザーバ室、
１０……ベースバルブ、１４……Ａ室、３２……
リーフバルブ、３８……シート面、４０……リー
フバルブシート、４２……ワツシヤプレート、４
４……バルブガイド、４６……軸部、５０……か
しめ部、５２……段付部、５６，５８……面取
り、６０……ガイド部。
Fig. 1 is a sectional view of the base valve portion of a hydraulic shock absorber according to an embodiment of the present invention, Fig. 2 is an enlarged sectional view of the washer plate and its vicinity in Fig. 1, and Fig. 3 is the same as Fig. 1. FIG. 4 is a cross-sectional view of the vicinity of the washer plate of a conventional hydraulic shock absorber. 4... Inner cylinder, 6... Outer cylinder, 8... Reservoir chamber,
10... Base valve, 14... Chamber A, 32...
Leaf valve, 38... Seat surface, 40... Leaf valve seat, 42... Washer plate, 4
4... Valve guide, 46... Shaft portion, 50... Caulked portion, 52... Stepped portion, 56, 58... Chamfer, 60... Guide portion.
Claims (1)
付部を形成した環状のベースバルブと、該ベー
スバルブに開口したポートを弾性的に開閉する
環状のリーフバルブと、該リーフバルブの底面
側の内周部位に配設された環状のリーフバルブ
シートと、該リーフバルブシートの底面側に配
設された環状のワツシヤプレートと、前記環状
のベースバルブ、リーフバルブ、リーフバルブ
シートおよびワツシヤプレートに嵌入する軸部
を備えたバルブガイドとを有し、前記バルブガ
イドの一端に設けたフランジ部と他方の軸端部
に軸方向の圧縮力をかけて形成したかしめ部と
の間に前記ベースバルブ、リーフバルブ、リー
フバルブシートおよびワツシヤプレートを挾持
させた油圧緩衝器において、前記ワツシヤプレ
ートの前記リーフバルブ側の内周角部に前記ベ
ースバルブの段付部と同程度の大きさの面取り
を設けたことを特徴とする油圧緩衝器。 (2) 前記ワツシヤプレートを、ばね鋼等の硬い変
形しにくい材料から構成した実用新案登録請求
の範囲第１項記載の油圧緩衝器。 (3) 前記ワツシヤプレートの前記かしめ部側の内
周角部にも面取りを設けた実用新案登録請求の
範囲第１項記載の油圧緩衝器。 (4) 前記ワツシヤプレートの、前記リーフバルブ
側の面取りと、前記かしめ部側の面取りとを、
同一寸法の面取りから構成した実用新案登録請
求の範囲第３項記載の油圧緩衝器。 (5) 前記ワツシヤプレートの内周に、前記リーフ
バルブ側の面取りと前記かしめ部側の面取りと
の間に、前記バルブガイドの軸部の外周を摺接
するガイド部を設けた実用新案登録請求の範囲
第１項記載の油圧緩衝器。[Claims for Utility Model Registration] (1) An annular base valve that is attached to the bottom of the inner cylinder of the shock absorber and has a stepped part formed on the inner periphery of the bottom surface, and a port opened in the base valve that elastically opens and closes. an annular leaf valve; an annular leaf valve seat disposed on the inner peripheral portion of the bottom side of the leaf valve; an annular washer plate disposed on the bottom side of the leaf valve seat; It has a base valve, a leaf valve, a leaf valve seat, and a valve guide equipped with a shaft part that fits into the washer plate, and an axial compressive force is applied to the flange part provided at one end of the valve guide and the other shaft end part. In the hydraulic shock absorber, the base valve, the leaf valve, the leaf valve seat, and the washer plate are sandwiched between the caulked portion formed by applying the above-mentioned A hydraulic shock absorber characterized by having a chamfer of the same size as the stepped portion of the base valve. (2) The hydraulic shock absorber according to claim 1, wherein the washer plate is made of a hard material that does not easily deform, such as spring steel. (3) The hydraulic shock absorber according to claim 1, wherein a chamfer is also provided on an inner circumferential corner portion of the washer plate on the caulking portion side. (4) A chamfer on the leaf valve side of the washer plate and a chamfer on the caulking part side,
The hydraulic shock absorber according to claim 3, which is constructed from chamfers of the same size. (5) A request for registration of a utility model in which a guide portion is provided on the inner periphery of the washer plate, between the chamfer on the leaf valve side and the chamfer on the caulking portion side, the guide portion slidingly contacts the outer periphery of the shaft portion of the valve guide. Hydraulic shock absorber according to item 1.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985199349U JPH0231615Y2 (en) | 1985-12-26 | 1985-12-26 | |
| DE8686117922T DE3666613D1 (en) | 1985-12-26 | 1986-12-23 | Twin-tube type shock absorber with a base valve portion structure coupled by caulking |
| EP86117922A EP0230042B1 (en) | 1985-12-26 | 1986-12-23 | Twin-tube type shock absorber with a base valve portion structure coupled by caulking |
| US07/171,186 US4815576A (en) | 1985-12-26 | 1988-03-18 | Twin-tube type shock absorber with a base valve portion structure coupled by caulking |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985199349U JPH0231615Y2 (en) | 1985-12-26 | 1985-12-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62107131U JPS62107131U (en) | 1987-07-08 |
| JPH0231615Y2 true JPH0231615Y2 (en) | 1990-08-27 |
Family
ID=16406284
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985199349U Expired JPH0231615Y2 (en) | 1985-12-26 | 1985-12-26 |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US4815576A (en) |
| EP (1) | EP0230042B1 (en) |
| JP (1) | JPH0231615Y2 (en) |
| DE (1) | DE3666613D1 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3009151B2 (en) * | 1988-04-04 | 2000-02-14 | 株式会社ユニシアジェックス | Hydraulic shock absorber |
| US5118120A (en) * | 1989-07-10 | 1992-06-02 | General Electric Company | Leaf seals |
| US5060689A (en) * | 1989-08-24 | 1991-10-29 | Ced's, Inc. | Universal check valve assembly |
| DE4406349C2 (en) * | 1994-02-26 | 1997-04-03 | Fichtel & Sachs Ag Werk Eitorf | Telescopic vibration damper |
| DE4423658C2 (en) * | 1994-07-06 | 2000-06-21 | Daimler Chrysler Ag | Hydraulic power steering |
| US6289571B1 (en) * | 1997-05-16 | 2001-09-18 | Yamashita Rubber Kabushiki Kaisha | Manufacturing process of antivibration device |
| US6230858B1 (en) * | 1999-08-31 | 2001-05-15 | Delphi Technologies, Inc. | Internally slotted orifice disc for low speed control in automotive dampers |
| DE10000179A1 (en) * | 2000-01-05 | 2001-07-26 | Krupp Bilstein Gmbh | Two-tube shock absorbers |
| DE10011168C1 (en) * | 2000-03-08 | 2001-09-06 | Mannesmann Sachs Ag | Damper valve has axial through flow ducts partly covered by valve disc, outlets, feeder opening, funnel, curved section and arm |
| JP2004211879A (en) * | 2003-01-08 | 2004-07-29 | Showa Corp | Bottom valve device of hydraulic shock absorber |
| TWM285363U (en) * | 2005-05-25 | 2006-01-11 | Jong-Jyr Kau | Improvement of steps machine structure |
| US8342303B2 (en) * | 2006-07-28 | 2013-01-01 | Hitachi, Ltd. | Valve apparatus |
| CN100493827C (en) * | 2007-07-20 | 2009-06-03 | 隆昌山川减振器工业有限公司 | Technique for assembling subassembly of bottom valve of condensation damper valve in hydraulic damper |
| US20100011681A1 (en) * | 2008-07-21 | 2010-01-21 | Wei-Hua Chiang | Shock Absorber |
| JP5755616B2 (en) * | 2012-08-31 | 2015-07-29 | 株式会社ショーワ | Hydraulic shock absorber and valve |
| DE112020003585T5 (en) | 2019-07-26 | 2022-04-14 | Hitachi Astemo, Ltd. | Arrangement, shock absorber and method of manufacturing the arrangement |
| DE102019131319A1 (en) * | 2019-11-20 | 2021-05-20 | Thyssenkrupp Ag | Vibration damper and motor vehicle with such a vibration damper |
| CN111706489B (en) * | 2020-03-18 | 2025-01-10 | 浙江品达机动车部件有限公司 | Environmentally friendly and energy-saving electric vehicle vacuum pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2159289A (en) * | 1937-03-15 | 1939-05-23 | Monree Auto Equipment Company | Valve construction |
| GB676521A (en) * | 1948-11-08 | 1952-07-30 | Brouwer Davis Mcintyre | Shock absorber construction |
| US2626685A (en) * | 1950-10-14 | 1953-01-27 | Gen Motors Corp | Shock absorber |
| DE958532C (en) * | 1953-11-27 | 1957-02-21 | Volkswagenwerk G M B H | Valve for hydraulic shock absorbers of motor vehicles |
| DE2355254A1 (en) * | 1972-11-09 | 1974-05-22 | Allinquant F M | HYDRAULIC TELESCOPIC SHOCK ABSORBER AND SUSPENSION ARRANGEMENT WITH SUCH A SHOCK ABSORBER |
| US3869956A (en) * | 1973-04-02 | 1975-03-11 | Avco Corp | Pin assembly rivet |
| FR2312925A7 (en) * | 1975-05-07 | 1976-12-24 | Allinquant Fernand | Shock absorber for road vehicle - has piston with twelve axial bores covered by disc springs |
| US4146118A (en) * | 1978-02-14 | 1979-03-27 | Zankl Robert H | Brake shoe assembly |
| US4221041A (en) * | 1978-10-02 | 1980-09-09 | Boeing Commercial Airplane Company | Semi-tubular rivets and method of using |
| JPS597853B2 (en) * | 1979-11-26 | 1984-02-21 | 株式会社昭和製作所 | Hydraulic shock absorber damping force generator |
| DE3202721C2 (en) * | 1982-01-28 | 1986-09-11 | August Bilstein GmbH & Co KG, 5828 Ennepetal | Pressure stage valve for hydropneumatic vibration dampers, especially bottom valve |
| JPS5932743A (en) * | 1982-08-14 | 1984-02-22 | Matsushita Electric Works Ltd | Solar heat collecting roof |
-
1985
- 1985-12-26 JP JP1985199349U patent/JPH0231615Y2/ja not_active Expired
-
1986
- 1986-12-23 EP EP86117922A patent/EP0230042B1/en not_active Expired
- 1986-12-23 DE DE8686117922T patent/DE3666613D1/en not_active Expired
-
1988
- 1988-03-18 US US07/171,186 patent/US4815576A/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP0230042A1 (en) | 1987-07-29 |
| JPS62107131U (en) | 1987-07-08 |
| DE3666613D1 (en) | 1989-11-30 |
| US4815576A (en) | 1989-03-28 |
| EP0230042B1 (en) | 1989-10-25 |
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